Brake



April 23, 1935. L. c. BRlssoN 1,998,533

BRAKE Filed Nov. 16, 1933 2 Sheets-Sheet 1 of @HSSOVL April 23, 1935. L. c. BRISSON BRAKE 2 Sheets-Sheet 2 Filed NOV. 16, 1953 l rfssam Patented pr. 23, 1935 UNITE n rice assignor to Socit Freins Hydrauliques France Anonyme: Socit des S. de Lavaud, Parle,

Application November 16, 1933, Serial No. 698,353

l In France November 1'1, 1932 13 Claims.

Brakes are already known comprising a drum, expansible braking means such as brake shoes for instance, and two entirely distinct devices for controlling these expansible braking means, one of these devices being of the hydraulic type and the other of the mechanical type.

Brakes of this kind have some inconveniences. The main inconvenience of said brakes consists in that the hydraulic device, on the one hand, and the mechanical device' on the other hand, do not act at the same place on the brake shoes. Now, in many cases, and particularly in the case of self-applying brakes, the braking action is quite different according to the position of the point of application of the stresses spreading the brake shoes apart.

A rst object of the invention is to avoid this inconvenience and to provide a brake of the type indicated in which the points of application on the brake shoes of the stresses spreading them apart are the same, whether these stresses are transmitted by the hydraulic device or by the mechanical device.

A second object of the invention is to provide a brake of the type indicated, in which the slack adjusting system operates in all cases, whether the stresses spreading the brake shoes apart are transmitted by the hydraulic device or by the mechanical device.

The accompanying drawings illustrate, by way of example only, a form of carrying the invention into practice.

Fig. 1 is an elevation of the apparatus, and the brake drum is assumed to be sectioned.

Fig. 2 is a side view corresponding to Fig. 1, with partial section made according to line II-II of Fig. 1.

Fig. 3 is a sectional plan view made according to line III-III of Fig. 1, and on an enlarged scale.

Fig. 4 is a partial rear elevation, according to the arrow IV of Fig. 2.

Fig. 5 is a partial sectional view made accord.

ing to line V--V of Fig. 3.

Fig. 6 is a sectional view made according to line VI-VI of Fig. 4.

The rotating drum is indicated at I. In this example, the brake is assumed to be a brake for motor vehicles, although the invention is utilizable for any application. The drum I has therefore, in this example, the usual shape of the brake drums of motor cars, and i't is adapted to be secured on a wheel bythe usual means; These means have not been shown, and in Figs. 2 and 3 have simply been illustrated the holes pro- (Cl. 18S-106) vided in the drum I and through which can pass the bolts used for securing said drum to the wheel or to the wheel hub, l designates the xed cheek member which is also common in the brakes of motor vehicles and ordinarily g;

brake control members and the brake shoes, and also to close the brake drum in order to avoid the entrance of mud and dust in the latter. The means for securing said serves to support the cheek member have not been shown, and at 5 10 and 6, etc., there have simply been indicated the holes through which the securing bolts can pass.

The invention is applicable whatever may be the expansible braking ment, upon braking, with the brake drum I In the example chosen, these expansible braking means are constituted by two brake shoes 1 and 8 connected together by links 9 and III which are pivoted to the lower end of the at II'and I2.

At the upper part, a spring I3, which enters holes I4 and I5 provided in lugs I6 and I1, con@ stantly tends to move the brake shoes towards each other. The brake shoes vided with bearing members I8 and I9 made o harder metal, and secured in any manner whatever, for instance by means of rivets 2U and 2l. These bearing memberaas will be described hereinafter in greater detail, are adapted to come 30 in contact with the pistons 22 and 23 of the actuating mechanism indicated at 24. In this arrangement, the surfaces of the pistons 22 and 23 on which bear the members I8 and I9 are plane, the pistons 22 and 23 are guided at right 35 angles to the direction of these planes, that is to say parallel to the links 9 and IIJ. Consequently, all the reacting stresses exerted on the brake shoes 1 and 8 by the control member 24,

by the links 9 and I0, and by the braking torque, 40

have constant and parallel directions so as to obtain the advantages of the 'brake described in the United States patent application in the name of Dimitri Sensaud de Lavaud, Serial No. 408,125, led November 18, 1929, for hicles. But it vmust be once again clearly understood that the invention is applicable to any other brake device; in fact, it does not reside in the brake itself, but in the means for actuating the brake, as will now be seen.

The device 24, which is illustrated in detail in Figs. 3, 4, 5 and 6, is composed of a body 25 secured on the cheek member 4 within the brake drum. This body 25 isy cylindrically Abored accordng to two parallel geometrical axes at means coming in engage- 1s brake shoes 20 1 and 8 are pro 25 Brakes for ve- 45 and at 21. The piston 23 slides in the bore 26 and the piston 22 in the bore 21. The piston 22 is provided with a head 28 limiting its inward movement, whilst the piston 23Abears against an abutment 29 which presses upon an inner partition 36 of the body 25. The pistons 22 and 23 are thus therefore co-axially guided in a fixed direction. Their end surfaces 3| and 32 are at right angles to this guide direction, and the body is so secured within `the cheek member 4 that, this guide direction is parallel to the links 9 and I0.

The piston 23 is provided, at 33, with a longitudinal slot in which extends a guide member 34 secured on the body 25, by means of a screw for instance. The piston 23 can therefore slide but it cannot rotate. Besides, the piston 23 is axially perforated with a hole 35 which is screwthreaded for receiving the screw-threaded end 36 of a member 31. This member is perforated with a radial hole 38 within which fits a pivot 39 for a pawl 40. The pawl- 40 cooperates with teeth 4I formed on the abutment member 29. This abutment member has been forcibly fitted in position, so as to be unable to rotate. A spring 4I always tends to cause the pawl 40 to rotate in the direction of the arrow 42. This arrangement provides the slack-adjusting device forming the subject-matter of the United States patent in the name of Dimitri Sensaud de Lavaud,

numbered 1,971,643 and dated August 28, 1934, for Automatic adjusting device.

A member 43 is secured within the body 25, for instance by means of a screw 44 and of an element 45 forcibly fitted in position. The member 43 carries, at 46, a pivot pin for a lever composed of two cheek members 41a, 41b, connected together for instance by means of two pins 48 and 49, one of which, 48, serves as a pivot for a bent lever 50, whilst the other, 49, serves as a pivot for a link 5I pivotally connected at 52 to the piston 22. 'I'he lever 50 carries, at 53 and 54, pivot pins for rollers 55 and 56, the roller 56 bearing on the end of the member 31, whilst the roller 55'bears on a thrust member 51 which will be described later on.

The device which has just been described is already known per se and does not form a part of the present invention. It is particularly described in a French patent filed by the Socit des Freins Hydrauliques S. de Lavaud, on the 3rd November 1931 and bearing No. 741,131.

Outside the xed cheek member 4 isV secured a support 58. Said support is bored at 59 for receiving a bush 60. A cap 6I rests on the support 58 and bush 60, so as to enclose and to tightly and hermetically secure a thick rubber diaphragm 62, of hemispherical shape. The cap 6| is perforated at 63 with an orifice through which is admitted a hydraulic pressure generated in any manner whatever and which need not be described herein. Moreover, the use of a distortable rubber wall such as 62 is also already known. Under the action of the hydraulic pressure, this wall bulges and pushes a piston 64 which is in contact with the thrust member. 51 by its periphery, as said thrust member 51 is hollow.

The member 51 is provided at 65 and 66 with longitudinal grooves through which passes a vertical shaft 81. 'I'his shaft 61 rotates in bearings 63 and 69 formingva part of the support 58. At its upper end, the shaft 61 is held from endwise movement by a washer 16 and a pin 1I. At its lower part, the shaft 61 receives an operating lever 12 secured on the same by a key 13. Finally, within the hollow thrust member 51, the shaft 61 is provided with a cam 14 acting onthe bot'- tom of the member 51.

Preferably, the cam 14 is given the shape of an arc of evolvent, the evolute of which would be a circle having for center the axis of the shaft 61, and, moreover, said shaft 61 is so arranged that the contact between the cam 14 and the member 51 takes place at a point 15 which is situated on the geometrical axis of this cylindrical member 51. It is then obviously necessary that the axis of the shaft 61 should not meet the axis of the member 51; the distance between both these axes is the radius of the circle of which the cam 14 is an evolvent. In these conditions, it will be seen that the thrust exerted by the hydraulically actuated piston 64 and the thrust exerted by the mechanically actuated cam 14, have exactly the same direction, which is that of the axis of the member 51, and have also exactly the same effects, since the mechanical control and the hydraulic control both always axially act on the member 51. It is obvious that the actuation of the cam 14 by the shaft 61 has no effect on the hydraulic control; on the other hand, it is also obvious that the actuation of the hydraulic control has no effect on the mechanical control.

The operation is as follows:

It will be assumed that the drum I rotates in the direction of the arrow 16 (Fig. 1) and that a hydraulic pressure is produced, which pressure, through the orifice 63, causes the thick diaphragm 62 to bulge. lThe piston 64 moves, and drives the member 51. This movement of the member 51 has no influence whatever on the mechanical control, since said member can freely slide owing to the grooves 65 and 66. The member 51 exerts .a thrust on the roller 55, this tending to cause the lever 50 to rotate about the pivot pin 46.

The movement of the lever 50 candetermine two movements. In fact, it will be assumed that the piston 22 is fixed. (it will be seenlater on that it is indeed the case in the example under consideration). Then, the triangle 52, 49, 46, which has two fixed apices at 52 and at 46, also renders the apex 49 fixed. The lever 41o-41h cannot therefore move. The point 48 being fixed, the rotation of the lever 50 exerts a thrust on the member 31 and, consequently, on the piston 23. The piston pushes therefore the member I9, that is to say, the brake shoe 8 which moves away and presses against the wall of the brake drum. This brake shoe tends to be driven by the rotation of the drum I, and this stress is transmitted, by the links 9 and I3, to the brake shoe 1. The latter bears upon the piston 22, and tends to cause it to enter the body 25 which is impossible owing to the abutment 28. 'I'he operation of this type of self-applying brake is well known and need not be further described.

Normally,`the piston 23 must not move to an extent greater than the height of a tooth of the series of teeth. Consequently, in the normal case, during the movement of the piston 23, the pawl 40, held in contact with a tooth by the contact 42, slides on this tooth without leaving it. On the contrary, if the movement of the piston 23 is oi' greater amplitude, the pawl 40 moves away from the teeth and comes in engagement with the following tooth. When the piston 23 returns to its original position under the action of the returning spring I3, owing to the fact that the pawl 46 has come in engagement with the following tooth, its propping action on this tooth forces the member 31 to rotate. The rotation of the member 31 is such that it causes the screw 3B to unscrew relatively to the piston 23, so that the piston 28 `tion in the name of Dimitri Sensaud de Lavaud,

Serial No. 422,662 tiled on November 22, 1930.

If instead of acting on the hydraulic means, the lever 12 had been actuated by a linkwork (not shown), this leverby rotating would have exerted, through the cam 14, an axial thrust on the member 51 and the operation would have been identically the same. It will be noted, in particular. that slack-adjustment would have taken place identically in the same manner.

In case the drums rotate in reverse direction to the arrow 16, the piston 23 becomes xed. At this moment, it is the pivot pin 54 which must be considered as movable, and it will then be seen that the thrust of the member 51 onthe roller 55 pushes the piston 22 outwardly. This case is that of backward running, it is identical to the preceding case, with this diiIerence, however, that the slack-adjusting device does not operate. It will operate upon the next application of the brake during forward running.

The entire set of members is secured in position by means of screws such as 18, 18, 8U and 8|, these screws pass through the cap 6i, body 58, cheek member 4, and screw into the body 25. A fluid-tight packing is provided at 82. The ring 83 which loosely i'lts on the body 25, serves to ensure the centering relatively to the hole 84 which is drilled in the cheek member 4 for allowing the passage of the member 51.

What I claim as my invention and desire to secure by Letters Patent is:

l. In a brake having a hydrauliccontrol and a mechanical control, a rotating drum, expansible braking means, a thrust member, means for guiding the thrust member in a direction at right angles to the direction oi expansion of the expansible braking means, means for transmitting to the expansible braking means the movement of said thrust member, hydraulic means and mechanical means arranged for separately acting on said thrust member.

2. In a brake having a hydraulic control and a mechanical control, a rotating drum, expansible braking means, a thrust member, means for guiding the thrust member in a direction at right angles to the direction of expansion of the ex` pansible braking means, means for transmitting to the expansible brakingmeans the movement of said thrust member, hydraulic means and mechanical means arranged for separately exerting a thrust, according to one and the same geometrical axis, on said thrust member.

3. In a brake having a hydraulic control and a mechanical control, a rotatingdrum, expansible braking means, a thrust member, means for guiding the thrust member in a direction at right angles to the direction of expansion of lthe expansible braking means, means comprising an -automatic wear-compensating device, for transmitting to the expansible braking means the movement of said thrust member, hydraulic means and mechanical means arranged for separately acting on said thrust member.

4. In a brake having a hydraulic control and a mechanical control, a rotating drum, expansible braking means, a thrust member, means for guiding the angles to the direction of expansion of the exthrust member in a direction at right pansible braking means, means comprising an automatic wear-compensating device, for transmitting to the expansible braking means the movement of said thrust member, hydraulic means and mechanical means arranged for sepi arately exerting a thrust, according to one and the same geometrical axis, on said thrust member.

5. In a brake having a hydraulic control and a mechanical control, a rotating drum; brake shoes, a thrust member, pistons co-axially "guided for acting on the ends of the brake shoes, means for transmitting to the pistons the movement of said thrust member, said means comprising an automatic wear-compensating device, hydraulic means and mechanical means arranged for separately acting on said thrust member.

6. In a brake having a hydraulic control and a mechanical control, a rotating drum, brak shoes, a thrust member, pistons co-axially guided for acting on the ends of the brake shoes, means for transmitting to the pistons the movement of said thrust member, said means comprising an automatic wear-compensating device, hydraulic means and mechanical means arranged for separately exerting a thrust, according to one and the same geometrical axis, on said thrust member.

'1. In a brake having a hydraulic control and a mechanical control, a rotating drum, brake shoes, a thrust member, pistons co-axially guided for acting on the ends of the brake shoes, means for guiding the thrust member in a direction at right angles to the direction in which the pistons are guided, means for transmitting to the pistons the movement of said thrust member, said means comprising an automatic wear-compensating device, hydraulic means and mechanical means arranged for separately acting on said thrust member.

8: In a brake having a Ihydraulic control and a mechanical control, a rotating drum, expan-l sible braking means, a thrust member, means for transmitting to the expansible braking means the movement of said thrust member, a hydraulically actuated piston arranged for acting on the periphery of the thrust member, means for exerting a mechanical portion of the thrust member.

9. In a brake having a hydraulic control and a mechanical control, a rotating drum, expansible braking means, a hollow thrust member provided with at least one side opening, means for transmitting to the expansible braking means the movement of said thrust member, a hydraulically actuated piston arranged for acting on the periphery of the hollow thrust member, a shaft arranged for rotating under the action of a mechanical control and passing through the opening of the hollow thrust member, a cam secured on said shaft for exerting a thrust on the bottom of the hollow thrust member.

10. In a brake having a hydraulic control and a mechanical control, a rotating drum, expansible braking means, a thrust member, means for guiding the thrust. member in a direction at right anglesto the direction of expansion of the expansible braking means, meansfor transmitting to the expansible braking means the movement of said thrust member, a hydraulically actuated piston arranged for acting on the periphery of the thrust member, and means for exerting a mechanical thrust action on the central portion of `the' thrust member.

' f* 1l. In a brake having a hydraulic control, and

thrust action on the central member, a cam secured on said shaft for exerting a thrust on the bottom of the hollow thrust member.

l2i In a brake having a hydraulic control and a mechanical control, a rotating drum, brake shoes,

Hwa

a hollow thrust member provided with at least one side opening, pistons-coaxially guided for acting on the ends of the brake shoes, means for guiding' the thrust member in a direction at right angles to the direction in which the' pistons are guided, means for transmitting to the pistons, the movement of said thrust member, said means comprising an automatic wear-compensating device, a hydraulically actuated piston arranged for 1 acting on the periphery of the hollow thrust member, a shaft arranged for rotating under the action of a mechanical control and passing through the opening of the hollow thrust member, a cam secured on said shaft for exerting a thrust on the bottom of the hollow thrust member.

13. In a brake having a hydraulic control and a mechanical control, a rotating drum, expansible i V braking means free within the rotating drum, a

thrust member, pistons co-axially guided for l pressing upon the ends o! the expansible braking i means and having abutment heads cooperating with xed abutments limiting the movement of the pistons towards each other, means for transmitting to the pistons the movement of said thrust member, a hydraulically actuated piston arranged for acting on the periphery oi the thrust i member, and means for exerting a mechanical thrust action on the central portion of the thrust member.

- LOUIS CHARLES BRISSON. 

